Method of and apparatus for processing linear elements

ABSTRACT

Method of and apparatus for processing linear material including rotary means for linearly feeding the linear material and rotary means for collecting the fed material where one of the two means is predeterminedly variable in its speed during advancement of the material; the other means to be matched thereto. The apparatus includes means for supplying a control signal having a patterned rate of change that is arranged to modify the speed of the other means to approach the speed of the one means and means for sening the difference between the linear rate of feed and collection. Means responsive to the sensed differences to bring the speed of the other means into conformity with the actual speed of the one means.

nited States Patet Kiink et al.

METHOD OF AND APPARATUS FOR PROCESSING LINEAR ELEMENTS -lnventors:Jerome P. Klink; Alex P. Symborski,

both of Granville; Norman R. Shape, Columbus, all of Ohio Owens-(ZorningFiberglas Corporation, Toledo, Ohio Filed: Oct. 4, 1973 Appl. No.:403,578

Related US. Application Data Continuation of Ser. No. 206,008, Dec. 8,1971, Pat. No. 3,771,324.

Assignee:

References Cited UNITED STATES PATENTS [451 Jan.21, 1975 Attorney,Agent, or FirmCarl G. Staelin; John W. Overman; Ronald C Hudgens [57]ABSTRACT Method of and apparatus for processing linear materialincluding rotary means for linearly feeding the linear material androtary means for collecting the fed material where one of the two meansis predeterminedly variable in its speed during advancement of thematerial; the other means to be matched thereto. The apparatus includesmeans for supplying a control signal having a patterned rate of changethat is arranged to modify the speed of the other means to approach thespeed of the one means and means for sening the difference between thelinear rate of feed and collection. Means responsive to the senseddifferences to bring the speed of the other means into conformity withthe actual speed of the one means 2 Claims, 18 Drawing Figures PATENTEDJANZI I975 SHEET 20F 6 DC VOLTAGE SOURCE a H w R f H L x 0 w y W a O M Cx h T J v j M 5 1l H E 0 T PO W5 M Z 7 1 m W F. E i

PAIENTEDJANZ 11915 :3, 86 1.609

. SHEET U UF 6 I /Z24 I i 2241 my I 51g} 1 PATENTED H 3,861 509 SHEEI 50F 6 Kai METHOD OF AND APPARATUS FOR PROCESSING LINEAR ELEMENTS This isa continuation-in-part of US. Pat. application Ser. No. 206,008 filedDec. 8, 1971 now U.S. Pat. No. 3,771,324.

BACKGROUND OF THE INVENTION This invention relates to production ofcontinuous filamenJs of a thermoplastic material and more particularlyto improvements for producing such filaments where production apparatususes mechanical attenuation of filaments from streams of heatedthermoplastic material. The invention is especially useful in producingcontinuous glass filaments and strands of these filaments.

Normally heated thermoplastic materials such as molten glass are drawninto continuous filaments from streams flowing from a feeder holding abody of the heated material. Usually apparatus attenuates the streamsinto individual continuous filaments and combines them into a bundle orstrand under the influence of pulling forces exerted directly by awinder. The winder collects the strand into a wound package on acollection tube mounted on a driven rotatable collet. The winderscommonly used can collect strands at linear strand speeds up to 10,000to 15,000 feet per min ute or more.

This well known process has inherent shortcomings that influence thefilaments, strands and wound packages. For example, the productionapparatus uses the winding package itself to provide the attenuatingforces. Consequently repeated wraps of strand on the package with highstrand tension gradually builds-up an increasing inward compressiveforce on the package. This compressive force can crush filaments andbuckle interior strand layers. Then too, tension in the strand can burystrand by squeezing strand portions of overlying layers between andbelow strand portions of underlying layers. The buried strand can not befreely withdrawn from the package; the entangled strand breaks. Also,the gradual build-up of the winding package effectschanges in the strandcollection speed for a given rotational speed of the winding collet. Thebuildup of a package increases its diameter and consequently itscircumference. And circumferential surface speed of a winding packageequals package circumference times the angular speed of the package.Hence, for a given angular collet speed the strand collection speed (andfilament attenuation speed) during package build-up increases towards amaximum speed at the end of a packaging cycle. Under these conditionsthe filaments are smaller in diameter at the end of a package cycle thanthey are at the beginning of the cycle. Some packages collect strand for60 minutes or more. Thus, speed differences (and hence filament diameterdifferences) can be considerable.

There have been attempts to overcome the difficulties. For instance,special complex collets have been made to apply an outward force againstthe inward compressive forces of a winding package. Such collets madepackage removal from collets easier but do not relieve tension within apackage. Consequently, the results have been far from satisfactory.

Efforts have been made to overcome filament diameter non-uniformity infilament forming operations by controlling the viscosity of the streamsand by attempting to keep a constant linear strand collection speed byvarying the collet speed during formation of a package. However, it hasonly been practical to make these viscosity and collet speed variationsin a linear fashion. But the collection speed variations during packagebuild-up change exponentially. Thus, prior efforts have not been fullysuccessful.

Efforts have been made to overcome compressive forces in a package fromstrand tension and to produce uniform filament diameters by use ofpulling wheels rotated at a constant rotational speed. Here the pullingwheels are between a stream feeder and a collecting device. This priorapparatus uses winders that rotate a collecting package on a collet orspindle with only sufficient force to take-up strand as strand is madeavailable to it by the pulling wheel. In these prior arrangements aconstant torque or constant horse power motor is normally used to rotatethe collet. Increased package size (mass) cause these motors to reducerotational speed and thus the tension in the collecting strands reduces.The apparatus does reduce high strand tensions (compressive forces) in awound package and produces filaments of uniform tension. But theapparatus does not control tension in a strand.

Further, prior apparatus has lacked stability in high speed strandcollection operations. The instability in operation of the apparatustends to produce linear strand speed variations that jerk strands. Sucha situation is particularly harsh on strand in processes using apparatusrequired to cooperate by matching linear strand speeds. And apparatusproducing strand speed changes can be especially disastrous to glassfilaments because they are essentially inextensible.

SUMMARY OF THE INVENTION An object of the invntion is improved methodand apparatus for forming continuous filaments from heated thermoplasticfilament forming material such as molten glass;

Another object of the invention is improved apparatus for formingcontinuous filaments from heated thermoplastic filament formingmaterial, such as molten glass, and subsequently combining the filamentsinto a strand and collecting the strand into a wound package at aselected tension.

Yet another object of the invention is improved apparatus for matchingstrand collection speed with a strand feed speed during collection of awound strand package.

Still another object of the invention is improved method and apparatusfor processing linear elements.

The above and other objects are attained by apparatus for and method ofcollecting linear material that includes means for linearly feedinglinear material and means for receiving the fed material where one ofthe means is predeterminedly variable in its linear speed duringadvancement of the material; the other means is to be matched theretoduring advancement of the material. The invention further includes meansfor sensing the differences between the speeds of the feeding means andthe receiving means and means effective in response to the senseddifferences between the speeds to bring the speed of the other meansinto conformity with actual linear speed of the one means.

Further, the objects embrace use of apparatus for packaging linearmaterial into a wound package that keeps linear material traversingapparatus in predetermined spaced relationship with packages duringcollection of the packages.

Other objects and advantages will become apparent as the invention isdescribed more clearly in detail with references made to theaccompanying drawings.

DESCRIPTION OF THE DRAWINGS FIG. 1 is a front elevation view ofapparatus embodying the principles of the invention. FIG. I shows acontinuous glass filament forming operation where a filament pullingdevice attenuates glass filaments and a take-up winder collects glassstrand as a wound package.

FIG. 2 is a side elevation view, partially in section, of the apparatusshown in FIG. 1. The section is taken along lines 2-2 in FIG. 1.

FIG. 3 is a back elevation view in section of the winder shown in FIGS.1 and 2. The section is taken along lines 33 in FIG. 2.

FIG. 4 is a plan view of the strand traversing portion of the windershown in FIGS. 1 through 3. The dashed lines indicate packages beingcollected by the winder.

FIG. 5 is a simple flow diagram of controls used with the apparatusshown in FIGS. 1 and 2.

FIG. 6 is a more detailed, but still simplified showing, of the controlsshown in FIG. 5.

FIG. 7 is a somewhat enlarged plan view of the strand engagingtransducer or sensor shown in FIGS. 1, 2 and 5 FIG. 8 is a frontelevation view of the transducer shown in FIG. 7 taken along the lines8-8.

FIG. 9 is a graph showing change in the diameter of a package duringcollection versus time. The graph generally shows the rate at which apackage builds-up during collection.

FIG. 10 is a modified transducer arrangement.

FIG. 11 is an embodiment of controls used to maintain the strandtraversing apparatus of the winder shown in FIGS. 1 through 3 at apredetermined spaced relationship with winding packages.

FIG. 12 is a view in elevation of drive apparatus for moving the strandtraversing support of the winder shown in FIGS. 1 through 3.

FIG. 13" is a side elevation view of the apparatus shown in FIG. 12.

FIG. 14 is a simplified front view in elevation of a continuous glassfilament forming apparatus using the winder shown in FIGS. 1 through 3.The winder is shown without use of a rotary filament pulling device.

FIG. 15 is a side view in elevation of the apparatus shown in FIG. 14.

FIG. 16 is a simple fiow diagram of controls for use with the apparatusshown in FIGS. 14 and 15.

FIG. 17 is a side elevation view of another embodiment of apparatusaccording to the principles of the invention in a continuous glassfilament forming operation.

FIG. 18 is a showing of controls used with the apparatus shown in FIG.17.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The method and apparatus of theinvention are particularly valuable in processes forming filaments fromheat softened fiber forming mineral material such as molten glass wheretemperature and filament processing speeds affect fiber diameter. Yet,method and apparatus embodying the principles of the invention are alsouseful in processing and packaging bundles of textile filaments madefrom other thermoplastic fiber forming materials. Thus, the disclosedglass fiber forming operation is only an example used to explain theoperation of the invention. The invention has wider application in avariety of filament forming operations and processing operations forlinear material generally.

The apparatus shown in FIGS. I and 2 show a continuous glass filamentforming operation embodying the principles of the invention. Theapparatus as shown uses a rotary-filament pulling device to formcontinuous glass filaments at a constant filament forming speed.Further, the apparatus, as shown, combines the filaments into twostrands and collects the strands below the rotary pulling device atselected strand ten sion. Normally such strand tension is less than thesum of the tension in the filaments above the rotary pulling device. Thefilament pulling device is between a collector and a source of moltenglass streams from which the glass filaments are drawn. Hence, thefilament pulling device isolates or separates the glass filament formingtension in the filaments above the device from the filaments collectedas strands below the device. Associated apparatus introduces apredetermined or selected tension, normally in the range of from 30 to200 grams, into the glass strands between the filament pulling deviceand the collector.

The collector matches the strand collection speed with the speed therotary pulling device feeds the strands to the collector.

The embodiment shown collects two packages; however, one can use theapparatus of the invention to collect one package or more than twopackages.

FIGS. 1 and 2 illustrate a container or feeder I0 that holds a body ofmolten glass. The feeder 10 can receive a continuing supply of moltenglass by several known ways. For example, a forehearth can supply moltenglass to the feeder 10 from a furnace heating batch materials to moltenglass. Also, a melter associated with the feeder 10 can supply moltenglass to the feeder by reducing glass marbles to a heat-softenedcondition. At the ends of the feeder are terminals 12 that connect to asource of electrical energy to heat the feeder 10 by conventionalresistance heating. Such heating keeps the molten glass in the feeder 10at proper fiberforrning temperatures and viscosities. The feeder 10 hasa bottom 14 with orifices or passageways for delivering streams 16 ofmolten glass from the feeder 10. As shown depending orifices projectionsor tubular members 18 define the openings in the bottom 14.

The feeder 10 is normally made of platinum or an alloy of platinum.

The molten glass streams 16 are attenuated downwardly into individualcontinuous glass filaments 20. Gathering shoes 22 and 24 below thefeeder 10 combine the continuous glass filaments 20 into two bundles orstrands 26 and 28 respectively.

Normally apparatus applies both water and a liquid sizing or otherprotective coating material to the filaments 20. As shown nozzles 30 and32 adjacent to the bottom 14 of the feeder 10 direct water spray ontothe continuous glass filaments 20 before the shoes 22 and 24 combine thefilaments 20 into the glass strands 26 and 28.

A sizing applicator 36 supported within a housing 38 just above thegathering shoes 22 and 24 applies a liquid sizing or other coatingmaterial to the swiftly traveling continuous glass filaments 20. Theapplicator may be any suitable type of applicator known to the art;however, the applicator 36 is shown as an endless belt moved throughliquid held in the housing 38. As the continuous glass filaments speedin touching relationship across the surface of the moving endless beltapplicator 36, some of the liquid on the surface transfers to them.

A pulling wheel 40 attentuates the continuous glass filaments 20 at aconstant speed from the molten glass streams l6 supplied by the feeder10. The pulling wheel 40 is rotatably mounted on a housing 42 locatedjust below the shoes 22 and 24. A motor 44 within the housing 42 rotatesthe pulling wheel at a constant high angular speed. In practice themotor 44 is normally an induction motor.

The pulling wheel 40 is normally about 12 inches in diameter. The motor44 can rotate the wheel 40 sufficiently fast to withdraw the continuousglass filaments 20 from the streams 16 at linear speeds up to 12,000feet per minute and faster.

As shown in FIGS. 1 and 2 the strands 26 and 28 proceed from the shoes22 and 24 over a strand alignment shoe 46 having circumferential grooves48 and 49 into contact with a smooth circumferential surface 45 of thepulling wheel 40. The shoe 46 aligns the paths of the traveling strandsfor spaced apart mutually parallel relationship on the smoothcircumferential surface 45 of the pulling wheel 40, the strands beingdisposed substantially parallel to the circumferential center line ofthe pulling wheel 40. In FIG. 1 the strands 26 and 28 come into contactwith the pulling wheel 40 at the right hand side of the wheel 40 andleave the wheel at its left hand side.

The alignment shoe 46 is somewhat to the right and above the pullingwheel 40.

From the pulling wheel 40 the strands 26 and 28 advance upwardly andturn over the top of a spool or roller 54 rotatably mounted on the endof an arm 56. The arm 56 is pivotally mounted on the housing 42. In FIG.1 the roller 54 and arm 56 are somewhat above and slightly to the leftof the pulling wheel 40. A spring 58 within the housing 42 biases thearm 56 in a clockwise direction as viewed in FIG. 1. The biasing forceof the spring 58 introduces selected tension into the traveling strands26 and 28. The introduced tension is selected to permit the build ofdesired stable wound packages.

The locations of the alignment shoe 46 and the roller 54 promotenon-slipping engagement between the wet traveling strands 26 and 28 andthe speeding peripheral surface 45 of the pulling wheel 40. Normally anengagement of the strands along from 60 to 80 percent of the length ofthe peripheral surface 45 is sufficient to insure non-slippingengagement between the surface 45 and the wet strands 26 and 28. Angle Ain FIG. 1 represents the angular engagement of the strands 26 and 28along the peripheral surface of the wheel 40. Angle A is normally from240 to 300; an angle of from 250 to 280 is normally preferred forpulling wheels having a diameter of 11 to 12 inches.

To promote non-slipping engagmeent between the wet strands 26 and 28 andthe pulling wheel 40, the wheel 40 as shown uses an annular layer 60 ofpolyurethane. The layer forms the smooth circumferential surface 45 ofthe wheel 40. At times it can be useful to control the surface finish,e.g., to somewhat roughen the circumferential surface 45, to enhanceengagement between the surface and the wet strands.

The diameter of the pulling wheel 40 and the increased non-slippingengagement from a surfacing layer like layer 60 enhances thenon-slipping filament pulling capacity of the wheel 40, which can beused in filament forming operations having filament forming tensions ashigh as 700 grams or higher. Filament forming tension is the total orsummation of tension in each of the filaments 20 above the applicator30.

The pulling wheel 40 feeds the strands 26 and 28 at a constant linearstrand speed to a winder below. The strands travel from the pullingwheel 40 across the roller 54 and strand alignment shoes 62 and 64 tothe winder 70.

The winder 70 collects the strands 26 and 28 as essentially identicalwound packages 72 and 74 respectively on collectors. These collectorsare shown as tubes 76 and 78 telescoped over a spindle or collet 80. Adrive within the winder 70 rotates the collet 80.

Strand traversing apparatus 82 of the winder 70 reciprocates the strands26 and 28 back and forth lengthwise of the packages 72 and 74 (collet80) to distribute the advancing strands on their respective packagesduring package formation. Strand movement effected by the strandtraversing apparatus 82 is a combination of a fast primary strandreciprocating motion and a slower secondary strand reciprocating motion.

One can better understand the strand traversing apparatus 82 by lookingat the apparatus shown in FIGS. 1 through 4. The strand traversingapparatus 82 includes strand guides 88 held in spaced relation adjacentto the packages 72 and 74 by a support arrangement. The guides 88 slidein a slot lengthwise of a horizontally extending tubular cam supporthousing 90 projecting from the frame 92 of the winder 70. Rotatablymounted within the support housing 90 are identical co-axially joinedtogether cylindrical or barrel cams 96 with surface guide grooves 98.Cam followers 100 connect the strand guides 88 with the grooves 98 ofthe barrel earns 96. As the cams 96 rotate, the strand guides 88reciprocate along the slot in the housing 90 lengthwise of the collet 80(packages 72 and 74). As shown the cam support housing 90 and the cams88extend co-axially. And the housing 90 extends in a direction parallel tothe collet 80 with its axis in the same horizontal plane with the axisof the collet 80.

As shown the strand guides 88 are hooked at their ends to keep thestrands 26 and 28 engaged.

As the cams 96 reciprocate the strand guides 88, the guides reciprocatethe strands 26 and 28 lengthwise of the collecting packages 72 and 74.

The winder 70 includes a drive arrangement comprising a motor/clutch 102within the winder housing 92. The drive arrangement effects rotation ofthe cams 96 and rotation of the collet 80 at a controlled speed ratio.The desired package design determines the ratio.

The motor/clutch drive 102 includes a constant speed electric motor 104that drives the rotor of an associated eddy-current clutch 106. Theclutch 106 has an output shaft 108. Magnetic forces within the clutch106 transfer torque from the rotor driven by the motor 104 to the outputshaft 108. In practice the motor 104 is an induction motor.

The motor/clutch 102 is a variable speed drive. In operation the speedof the motor 104 remains constant; however, changes in flux density(magnetic forces) within the clutch 106 vary the amount of the motorsconstant speed rotational energy output transferred to the output shaft108. The greater the flux density the larger is the percentage of motoroutput transferred to the output shaft 108.

The drive 102 rotates the collet 80 through a nonslipping belt 110connecting the output shaft 108 with a collet drive shaft 112 above thedrive 102. The rotating collet drive shaft 112 rotates the collet 80.The shaft 112 is co-axial with the collet 80 and is rotatably held by abearing mounting assembly 114.

Rotational energy from the collet drive shaft 112 moves the strandtraversing apparatus 82 through nonslipping belts 116 and 118. The belt116 connects the collet drive shaft 112 and a rotatably mounted idlershaft 119 of an idler assembly 120. The belt 118 connects the idlershaft 1 19 with a cam drive shaft 124 that connects to and rotates thecams 96. The drive shaft 124 is co-axial of the cams 96 and is rotatablymounted by a bearing support assembly 126 and the vertical end plate 128of a movable carriage 130.

As the packages 72 and 74 build on the rotating collet 80, the diameterof each of the packages increases. And for any given angular colletspeed an increase in package diameter increases the speed of thecircumferential or axial surface of each of the packages 72 and 74.Hence, the strand collection speed would increase with increasingpackage diameter if there were no offsetting reduction in the angularspeed of the collet 80.

Accordingly, the invention includes means for controlling the angularspeed of the collet 80 to offset increases in strand collection speedfrom increasing package size during strand collection. As shown,controls modify collet speed through the drive 102. Such controls areeffective to maintain a strand collection speed equal to the constantstrand supply speed from the rotating pulling wheel 40 throughoutbuild-up of the packages 72 and 74.

The controls include means for establishing a control signal effectiveto modify the rotational speed of the collet 80 in accordance with apatterned rate of change that, in general, will effect a packagebuild-up at a linear strand speed matched to the speed of strand feed.The controls further include means for sensing the differences betweenthe linear rate of supply and linear rate of collection and meanseffective in response to such sensed speed differences to modify thepatterned rate of change of the control signal to bring the linear rateof strand collection into conformity with the actual linear rate ofstrand supply from the pulling wheel 40 throughout build-up of thepackages 72 and 74. The result is a substantially constant linear strandcollection speed throughout build of the packages 72 and 74.

In a broad sense, the invention includes means for linearly feedinglinear material and means for receiving the fed material where one ofthe means (either the feeding means or the receiving means) ispredeterminedly variable in its speed during advancement of the materialand the other means is to be matched thereto. To effect the matching theinvention includes control means supplying a control signal having apatterned rate of change that is effective to modify the speed of thematching speed means to approach in general the speed of thepredeterminedly variable speed means. Further, the invention providesmeans for sensing the differences between the speeds of the feedingmeans and receiving means and means effective in response to the sensedspeed differences to bring the matching speed means into conformity withthe actual speed of the predetermined variable speed means.

FIG. 5 shows a general block diagram embodiment of controls according tothe principles of the invention. In the embodiment a controller 140varies voltage signals to the eddy-current clutch 106 to control therotational speed of the collet during collection of the wound packages72 and 74. In the embodiment the controller receives voltage signalsfrom a sensing transducer 142 and receives a constant DC voltage signalfrom a suitable DC source such as a battery 144. The changing outputvoltage of the controller 140 controls the magnetic field strength ofthe eddy-current clutch 106 to effectively match the strand collectionspeed with the strand supply speed as the packages 72 and 74 increase indiameter. For improved stability the controller 140 receives feedbackvoltage signals from a tachometer 146; the tachometer signals are ameasureent of the actual angular speed of the clutch output shaft 108(and hence the collet 80).

Referring to FIG. 6, the controller 140 includes an integrator 150, amajor summing junction 3., and an amplifier 154. The integrator 150includes resistance 156 in a line 158, an operational amplifier 160 andan integrating capacitor 162 bridged between the input and output of theoperational amplifier 160. A line 164 connects the output of theoperational amplifier 160 (integrator 150) with the summing junction J Aline 166 connects the summing junction J with the amplifier 154. Apackage build switch 167 is in the line 164 between the junction J andthe integrator 150.

The battery 144 supplies a constant voltage to the summing junction Jthrough a line 168.

The tachometer 146 supplies its signal to the summing junction J througha voltage divider 170. e.g., a potentiometer, in a line 171. The settingof the voltage divider establishes the operating rotational speed of thecollet 80 at the start of package build.

The voltage from the summing junction J in line 166 is the algebraicsummation of all the voltages supplied to the junction J As illustratedthe voltage applied to junction J, by the battery 168 is positive; thevoltage applied to junction J by the integrator 150 is a generallyincreasing negative voltage; the voltage applied to junction J, by thetachometer 146 is a negative voltage.

The increasing negative voltage from the integrator 150 reduces thevoltage from the junction J, (the controller 140) throughout thebuild-up of the packages 72 and 74. Hence, the reducing voltage from thecontroller 140 correspondingly reduces the rotational speed of thecollet 80 during package collection.

The amplifier 154 amplifies the voltage signals from the junction J, toput them at proper strength for use by the eddy-current clutch 106.

The integrator 150 provides a steadily changing electrical output signalthat increases proportionately to the negative time integral of inputvoltage. Hence, for a given constant input voltage the integrator 150supplies an output voltage that has a polarity opposite to the inputvoltage and that builds (increases) linearly with respect to time.Accordingly, for a given constant positive input voltage the outputvoltage from the integrator 150 increases in a negative direction at aconstant rate of change. For different positive input voltages thelinear rate of change of the integrator output voltage can be made rapid(asteep slope) with respect to time or made to be slower (a more gradualslope) with respect to time. For example, larger positive integratorinput voltages produce higher rates of output voltage change (a steeperslope) in the negative direction.

Suring package collection, the transducer 142 supplies changing inputvoltages to the controller 140 from ajunction J through line 158. Thejunction J receives negative DC voltage through a potentiometer 175 inline 176; negative voltage from a suitable source is applied to the line176 at L The junction J receives positive DC voltage in line 178 througha resistance 179; positive voltage from a suitable source is applied tothe line 178 at L The voltages from L and L oppose each other, and thereis no input voltage to the controller 140 when the voltage effected atjunction J is zero with respect to ground.

In the embodiment shown the transducer 142 includes the junction Jpotentiometer 175, the pivotally mounted arm 56 and its spool or roller54. The transducer 142 can be more fully understood by considering FIGS.7 and 8 together with FIG. 6. As shown the potentiometer 175 within thehousing 42 has a control shaft 182. The shaft 182 extends through thewall 184 of the housing 42 and holds the arm 56. The arm 56 is fixed onthe shaft 182. Hence, any pivotal movement of the arm 56 moves the shaft182 about its axis and accordingly modifies the output voltage of thepotentiometer 175.

The biasing force of the spring 58 urges the arm 56 to pivot about theshaft 182 in a clockwise direction (as viewed in the figures) into thestrands 26 and 28 turning on the roller or wheel 54. As shown a leverarm 188 is fixed at one end to the potentiometer control shaft 182. Thelever arm 188 extends from the control shaft 182 in a direction oppositeto the arm 56. The spring 58 connects to the lever arm 188 and producesa torque in the control shaft 182 urging the arm 56 into the strands 26and 28. Thus, the arm 56, shoe 54 and biasing arrangement form a sensorthat engages the strands 26 and 28 to sense the relationship between thestrand collection and feed speeds.

The transducer 152 has a no output voltage position for the arm 56 whereno current signals flow from the junction J In such a position, theoutput voltage from the potentiometer 175 and the voltage supplied tothe junction J from L effect a zero voltage at junction J In practice, ahorizonatl position from the arm 56 has provided a satisfactory nooutput voltage position for the transducer 142. Other no output voltagepositions can be used.

As the arm 56 is moved progressively downwardly from the horizontal, thepotentiometer 175 is arranged to give smaller negative output voltages.Consequently, an increasing positive current is applied to the line 158as the arm 56 moves progressively downwardly.

When the arm 56 moves above the horizontal position, the size of thevoltage applied at L, is sufficient to produce a negative voltage fromthe potentiometer 175 larger in magnitude than the positive voltageapplied at L Hence, when the arm 56 is above the horizontal position,negative current is applied to the line 158 from the junction JNormally, the arm remains below the horizontal during package build-up.Thus, the current applied to the line 158 is normally positive.

In operation the transducer 142 senses the relationship between thestrand feed rate of the pulling wheel 40 and strand collection rate ofthe winder and includes means that provides a signal in response to thesensed differences between the rate of feed and rate of collection ofthe material. When the strand collection speed is greater than thestrand supply speed, the length of the strands 26 and 28 shortensbetween the pulling wheel 40 and the packages 72 and 74. Hence, thestrands 26 and 28 pull the arm 54 downwardly (counter clockwise). Thenegative voltage from the potentiometer 175 becomes smaller. A largerpositive voltage is supplied to the controller 140 from the junction JOn the other hand, when the strand collection speed is less than thestrand supply speed, the length of the strands 26 and 28 increasesbetween the pull wheel 40 and the packages 72 and 74. Hence, the strands26 and 28, in a sense, develop slack that permits the biasing force ofthe spring 58 to-move the arm 56 upwardly. The negative voltage from thepotentiometer 175 becomes larger in magnitude. Accordingly, a smallerpositive voltage is supplied from the junction 1 to the controller 140.

In operation at the beginning of package build, the axial surfaces ofthe collectors 76 and 78 and the pulling wheel 40 are brought up toequal speeds with the switch 167 open. The switch 167 is closed and thebuild of the packages 72 and 74 begins. Immediately their diametersbegin to increase. And consequently the strand collection speed beginsto accelerate beyond the strand supply speed'from the pulling wheel 40.Quickly the accelerating strand speed shortens the lengths of thestrands 26 and 28 between the pull wheel 40 and winder 70. Theshortening strand length pulls the arm 56 downwardly below thehorizontal until the positive voltage from the transducer 142 to theintegrator 150 cuases the integrator 150 (controller 140) to provide acontrol voltage signal having a patterned rate of change with respect totime that reduces the speed of the collet 80 (through the eddy-currentclutch 106) in accordance with the build-up of the package at thatmoment. In this initial equilibruim condition the reducing angular speedof th collet 80 keeps the strand collection speed matched to the strandsupply speed from the pulling wheel 40. In other words, the patternedvoltage signal from the controller resulting from the initialequilibrium voltage supplied by the transducer 142 is effectiveinitially to keep the collection speed of the strands 26 and 28 equal tothe supply speed from the pulling wheel 40.

But the initial voltage output from the controller 140 reduces linearlywith respect to time and the build-up of the packages 72 and 74increases strand collection speed nonlinearly. Hence, the initial linearvoltage pattern from the controller 140 (established by the initialequilibrium voltage supplied by the transducer 142) is only in generalaccordance with the build-up of the packages. Thus, matching strandcollection and strand supply speeds is only temporary.

Package build is shown in FIG. 9. As one can see the build-up of thepackages 72 and 74 is the most rapid when package build begins. Packagebuild-up slows as the packages 72 and 74 become larger in diameter. Inpractice, it has been found that the changes (increases) in packagediameter during package build occur in a complex nonlinear manner havingboth parabolic and exponential characteristics. Hence, the curveillustrated in FIG. 9 has both exponential and paraboliccharacteristics.

Hence, the linear voltage slope from the controller 140 (integrator 150)established by the initial equilibruim transducer voltage is steeperthan required to keep the strand collection speed equal to the strandsupply speed. Therefore, the strand collection speed quickly becomesslower than the strand delivery speed from the pulling wheel 40. Slackdevelops in the strands 26 and 28 that permits the biasing force of thespring 58 to move the transducer arm 56 upwardly. Such upward movementof the arm 56 reduces the positive voltage from the transducer 142 untila new equilibruim condition exists. That is, the arm 56 is permitted tomove until the slope of the voltage from the controller 140 (integrator150) matches the rate of collet speed reduction with the rate of packagebuild-up at that moment.

Throughout build of the packages 72 and 74 equilibruim conditions arerepeatedly established. In the embodiment shown equilibruim conditionsare, for practical purposes, being continuously established. Under suchconditions the positive voltage from the transducer 142 to thecontroller 140 reduces throughout package build-up and the slope of thecontroller output voltage continuously changes from an initial steepslope to more gradual slopes.

In a sense one may consider the controls providing instantaneous controlvoltages changing with instantaneous rates of change matched withinstantaneous accelerations in the strands 26 and 28 throughout packagebuild. These control signals are effective to change the patterned rateof change of the control signal to maintain a substantially constantcollection speed equal to the strand feed speed from the pulling wheel40.

The summation of all the instantaneous voltage slopes from thecontroller 142 plots a curve in conformity with the curve of diameterchange with respect to time as shown in FIG. 9.

If necessary the controls can keep stable operation during times when anincrease in rotational speed of the collet 80 is needed. Such asituation occurs during times the collection speed is considerably belowthe feed speed from the pulling wheel 40. Slack in the strands 26 and 28allows the biasing force of the spring 58 to move the arm 56 above itsno voltage signal position (above the horizontal). A negative currentflows in the line 158. The growing negative integrator output signal isreduced. The output voltage from the controller 140 increases, whicheffects an increasing angular collet speed.

Normally, an increase in angular speed of the collet 80 is notnecessary. Hence, it is believed possible to use a transducer 142' asshown in FIG. 10. In the arrangement the potentiometer 175 supplies apositive voltage (applied across L and L directly to the controller 140.A transducer like the transducer 142 is preferred.

Under some circumstances it may be advantageous to bring the rates ofstrand collectionand delivery into conformity in response to differencesbetween them without changing the patterned rate of change of thecontrol signal. For example, one might regulate the electrical powersupply to the clutch 106 (and hence regulate the angular speed of thecollet 80) by supplying the signals from means sensing the differencesbetween the rates of strand delivery and collection (e.g., transducer142) directly to the summing junction J Accordingly, the patterenedsignal from the integrator 150 and the signals from the means sensingthe differences between the rates of strand delivery and collectioncombine at the summing junction J This variation in the speed controlsystem can be incorporated in the same unit as described above and mightbe resorted to as desired by operation of a snap switch or alternatelymight be accomplished automatically such as at the designed limits ofoperation by changing the patterened rate of change of the controlsignals.

It is believed possible to use other means for providing a controlsignal changing generally in accordance with the build-up of packageslike packages 72 and 74. For example, one might use an R-C circuithaving a condenser voltage curve for a given voltage changing at apatterned rate generally corresponding to the build-up of the packages.Means such as a transducer 142 and 142 would supply control signals tothe R-C circuit in response to sensed speed differences between thestrand supply and collection speeds to modify the reference voltage.Also, one might control the amplifier section of an integrator circuitin response to sensed speed differences effective to modifyamplification of an input voltage to provide a changing output signalthat effects a constant strand collection speed.

One might use other transducers. For example, one might use a transducerengaging the traveling strands 26 and 28 between the wheel 40 and winderto sense tension as an indication of the differences in the stranddelivery and collection speeds. One might use a transducer like thetransducer disclosed in US. Pat. No. 3,526,130.

The invention envisions a sensor for indicating the differences instrand collection and delivery speeds that does not engage the strands.For example, it is believed possible to use a doppler shift laser tomeasure differences in the circumferential surface speeds of the pullingwheel 40 and the packages 72 and 74.

The embodiment shown in FIGS. l-l0 uses the pulling wheel 40 to feedstrands at a constant speed to the winder 70; however, the inventionenvisions other embodiments, such as those discussed hereinafter, wherethe pulling wheel 40 or another strand feeding means supplies strands atvarious speeds. [n such situations, controls operate to match strandcollection speed with various strand feed speeds during packagecollection. Also, the invention embraces the use of the controls formatching the delivery speed of linear material with changing collectionspeeds of the material, e.g., rotating the collet at a constant angularspeed throughout package build.

The winder 70 senses the angular speed of the collet 80 as an indicationof the size of the packages 72 and 74 during collection and includesmeans responsive to sensed angular speed for effectively moving thestrand traversing apparatus 82 away from the collet 80 to maintain thetraversing guides 88 in predetermined spaced relation to theirrespective packages throughout collection of the packages. The hookedguides 88 move the engaging strands 26 and 28 with them as the hooksmove with the support arrangement during collection of the packages.

Controlling the relationship between the packages 72 and 74 and strandtraversing apparatus promotes inproved strand control throughout packagebuild and hence improved package build.

As more clearly seen in FlGS. 2 and 3, the carriage is movable on thewinder 70. And the cam housing 90 is carried by the carriage 130. Hence,the housing 90 moves with the carriage 130. The cam housing 90 andcarriage 130 move horizontally.

As shown the carriage 130 includes a base 190 in addition to thevertical end plate 128. The carriage 130 slides lengthwise on twohorizontal parallel support rods, rod 192 and 194, that are stationarywithin the winder 70. These rods extend through passageways in the base190; the passageways extend in a direction perpendicular to the axis ofthe collet 80 (packages 72 and 74). Hence, the carriage 130 and camhousing 90 are movable in a horizontal plane towards and away from thecollet 80 in a direction perpendicular to the axis of the collet 80. Thewinder frame 92 includes an elongated opening 191 permitting movement ofthe strand traversing apparatus 82 (cam housing 90).

FIGS. 11 through 14 show controls for positioning the carriage 130throughout package build-up to keep a predetermined spaced relationshipbetween the packages 72 and 74 and the strand traverse guides 88. Aswitch 198 completes the control circuit. The switch 198 can be manuallyclosed to complete the circuit or automatically closed to complete thecircuit when the collet 80 arrives at operating speed to begin packagecollection. Referring to FIG. 11, a battery 200 supplies a constantpositive DC voltage to a potentiometer 202. The output voltage of thepotentionmeter 202 travels to a summing junction J through a lead 204.The tachometer 146 provides a negative DC signal to the summing junctionJ through a lead 210. When the voltages supplied to the junction J 3 areunbalanced, the junction 1;, supplies an electrical signal through anoutput lead 212 (through switch 198) to a grounded solenoid coil orelectromagnet 216 that operates to close a normally open armature switch218. The switch 218 is in a circuit supplying electrical energy to amotor 220; a suitable commercial electrical source supplies electricalenergy to the circuit across L 3 and L The motor 220 is energized whenthe armature 218 is closed.

The energized motor 220 concurrently drives the slider of thepotentiometer 202 and actuates a drive system that moves the carriage130.

When the voltage from the potentiometer 202 and the tachometer 146 areequal, there is no electrical output from the junction J hence, thearmature switch 218, which is normally open, remains open. As thevoltage from the tachometer 146 decreases from the decreasing angularoutput speed of the clutch 106, the solenoid coil 216 becomes energizedfrom the higher voltage into the junction .1 from the potentiometer 202.The coil 216 closes the armature switch 218; and the motor 220 effectsmovement of the slider of the potentiometer 202 to reduce potentiometeroutput voltage until the output voltage is equal to the output voltagefrom the tachometer 146. The solenoid coil 216 then becomesde-energized. The armature switch 218 opens and the motor 220 becomesde-energized.

FIGS. 12 and 13 show more of the strand traverse position controlapparatus in a control box 224 mounted on the base 190 of the carriage130. Mounted near the top of the control box 224 is the electric motor220 with a sheave 226 on the output shaft 228 of the motor 220. Mountedbelow the motor 229 in the control box 224 is the potentiometer 202 witha sheave 230 on a slider control shaft 232 of the potentiometer. At thebottom region of the control box is a carriage drive including arotatably mounted drive screw 236 in a threaded passageway 238 in thebase 190 of the carriage 130. An unthreaded portion 242 of the drivescrew 236 carries sheaves 244 and 246.

The energized motor 220 rotates the drive screw 236 and moves the sliderof the potentiometer 202. A belt riding in sheaves 226 and 244 connectsthe motor output shaft 228 with the drive screw 236. A belt 252 ridingin sheaves 230 and 246 connect the drive screw with the slider controlshaft 232.

As the motor 220 rotates, the slider control shaft 232 moves the sliderof the potentiometer 202 and the drive screw 236. The rotating drivescrew 236 moves the carriage 130 away from the collet (collectingpackages) until the potentiometer voltage equals the voltage from thetachometer 146. The coil 216 then becomes de-energized; the switch 218then opens to de-energize the motor 220.

In practice the motor 220 is a slow rpm motor such as SLO-SYN made bythe Superior Electric Co.

An operator can select a desired position relationship between theguides 88 and collecting packages, e.g., packages 72 and 74. Because thecollet speed at the beginning of package collection is controlled andhence known, an operator can adjust a trim potentiometer 260 to bringthe voltage from the potentiometer 202 into balance with the knownbeginning voltage from the tachometer 146. Hence, the operator moves thecam housing 90 (carriage 130) to a selected location to position theguides 88. Such movement also moves the slider of potentiometer 202.Thus, the operator merely adjusts the trim potentiometer 260 to providevoltage from the potentiometer 202 at the beginning of package build-upthat matches the tachometer voltage.

The idler assembly permits movement of the carriage without parting thedrive belts 116 and 118. As shown the idler 120 includes the rotatableidler shaft 119, bearing box 270, position arm 272, support member 274and support bracket 276.

The support member 274 and bracket 276 hold the bearing box 270 andshaft 119 above the carriage 90. The bearing box 270 is movable aboutthe axis of the support member 274 by swing legs 277 and 278.

The position arm 272 connects the shaft 119 and cam drive shaft 124 tokeep these shafts at a constant spaced distance from the belt 118. Thearm 272 pushes (swings) the shaft 119 and its gear box upwardly aroundthe axis of shaft support member 274 as the carriage 130 moves towardsthe collet 80. The reverse is true as the carriage 130 moves away fromthe collet 80.

The swinging movement of the assembly 120 keeps both the belts 116 and118 in driving relationship on their respective sheaves.

The winder 70 provides for the slower secondary strand traversing motionby apparatus reciprocating the cam housing 90. Such apparatus includes amotor 280, spur gears 282 and 284, cam 286 and following 288. In theembodiment shown, the cam 286 is a wheel cam fixed on a rotatable shaft290. The motor 280 rotates the wheel cam 286 through the meshing spurgears 282 and 284. The follower 288 includes a pin 292 engaging theperipheral groove 294 on the wheel cam 286. The follower 288 is securedon the cam drive shaft 124. As the shaft 290 turns the wheel 286, thewheel reciprocates the follower 288. Hence, the cam wheel 286reciprocates the cam housing 90 through the follower 288. A conventionalspline arrangement (not shown) can be used to permit the shaft 124 tomove back and forth along its axis and still be driven in rotation.

One can use various cam wheels to provide secondary strand traversingmotions having different stroke lengths. In the embodiments shown inFIGS. 1 and 2 it has been useful to use a short secondary reciprocatingstroke length of from /2 inch and less.

The winder 70 is shown in combination with apparatus for modifying theangular speed of the collet 80 (packages 72 and 74) exponentially. Butthe winder 70 can be used with apparatus modifying the angular speed ofthe collet 80 in a linear fashion. Moreover, the winder 70 can be usedto pull linear elements from a source, e.g., pull glass strands withoutthe use of a filament pulling device like the pulling wheel 40.

FIGS. 14 and 15 illustrate the winder 70 without a pulling arrangementabove it. As shown a feeder 310 supplies molten glass streams 316 fromtips 318. The winder 70 withdraws continuous glass filaments 320 fromthe streams 316. Gathering shoes 322 and 324 combine the filaments 320into two strands, i.e., strands 326 and 328. A sizing applicator 336held in a housing 338 applies liquid sizing or other coating material.The strands 322 and 324 wind as packages 372 and 374.

In the embodiment shown in FIGS. 14 and 15 one can use known ways tomodify the speed of strand collection as the packages 372 and 374increase in size. FIG. 16 shows a control using the controller 140without a transducer. In FIG. 16 a source of DC voltage 380 supplies aconstant voltage input to the integrator 150.

FIGS. 17 and 18 show a modified embodiment of the glass filament formingapparatus shown in FIGS. 1 and 2. FIG. 17 shows the overall apparatus;FIG. 18 shows controls for the apparatus illustrated in FIG. 17.

The controls of FIG. 18 can be operated in two modes. The controls canbe switched to operate the apparatus as explained herein: so that thepull wheel 40 is rotated at a constant angular speed to feed the glassstrands 26' and 28' at a constant linear rate and so that the collet 80is rotated at various angular speeds to collect the strands 26' and 28'at a constant linear collection rate matched to the rate of strand speedduring formation of packages 72' and 74'. Also, the controls can beswitched to operate the apparatus: so that the collet 80 is rotated at aconstant angular speed, which effects a predeterminedly variableincrease in the linear rate of strand collection during package build-upand so that the pull wheel 40 is rotated at varying rotational speeds tofeed the strands 26' and 28 at a rate matched to the changing linearrate of a strand collection during package build-up.

So the embodiment shown in FIGS. 17 and 18 includes means for linearlyfeeding linear material and means for receiving the fed materials whereone of the two means is predeterminedly variable in its speed duringadvancement of such linear material; the other means to be matchedthereto. The apparatus includes means for supplying a control signalhaving a patterned rate of change that is effective to modify the speedof the other means to approach the speed of the one means and means forsensing the difference between the speeds of the feeding and receivingmeans. Means effective in response to the sensed differences between thespeeds changes the patterned rate of the control signal to bring thespeed of the other means into conformity with the actual speed of theone means.

The apparatus shown in FIG. 17 is the same as that shown in FIGS. 1 and2, except for the drive for rotating the pull wheel 40. Instead of themotor 44 shown in FIG. 2, the embodiment of FIG. 17 uses a a motor/-clutch assembly 402 to rotate the pull wheel 40. So the rotational speedof the pull wheel 40 can be varied during rotation. The assembly 402 isof the same type as the motor/clutch assembly 102 discussed in relationto the embodiment shown in FIGS. 1 and 2. As shown, the assembly 402includes a constant speed motor 404 and an eddy-current 406. And theoperation of the motor/- clutch assembly 402 is the same as themotor/clutch assembly 102.

Referring to the controls of FIG. 18, it can be seen that a single twoposition selector switch, denoted SS1, is used to select the mode ofoperation for the apparatus. As shown, the selector switch SS1 is a twoposition, 6 block switch like those commercially available frommanufacturers such as Cutler-Hamer, Inc. So one selector control switchinterlocks 6 individual switches; these switches are shown as SS1-1through SS1-6 in FIG. 18.

The controls of FIG. 18 includes means for driving one of either thecollet or the pull wheel 40 at various rotational speeds while drivingthe other at a constant rotational speed. The variable speed drive asshown includes the controller 140, clutch 106 and tachometer 146. Theconstant speed drive includes a constant speed regulator 410 receiving aconstant DC voltage from a suitable conventional DC voltage source 412.Through the selector switch SS1, the constant speed regulator 410 cancontrol the flux strength in either the clutch 106 for driving thecollet 80 or the clutch 406 for driving the pull wheel 40. The constantspeed controls also include a tachometer 414 that provides a feedbacksignal to the constant speed regulator 410.

The controls shown in FIG. 18 also include means for reversing theeffect of the potentiometer 175 on the controller as the potentiometeris moved by advancement of the strands 26 and 28 across the roller 54 ofthe arm 56.

With all the switches within the selector switch SS1 (switches SS1-lthrough SS1-6) in the full line position as shown in FIG. 18 thecontrols operate the apparatus of FIG. 17 like the apparatus of FIGS. 1and 2. That is the output of the constant speed regulator 410 isconnected with the clutch 406. So the pull wheel 40 is rotated at aconstant angular speed. And the output of the controller 140 isconnected with the clutch 106. So the rotational speed of the collet 80is changed during package formation as previously discussed herein tokeep the linear rate of strand collection in matched relationship withthe constant linear rate of strand feed from the pull wheel 40 duringpackage formation.

With the selector switch SS1 in the full line position, switches SS1-land SS1-2 place the potentiometer 175 in the same electricalcommunication with the junction J as shown in FIG. 6.

When all the switches of the selector switch SS1 (switches SS1-l throughSS1-6) are in the dashed line position as shown in FIG. 18, the collet80 is rotated at a constant rotational speed and the rotational speed ofthe pull wheel 40 is controlled to match the linear rate of strand fedwith the linear rate of strand collection as the packages 72 and 74'increase in'size during their formation. With the switches in the dashedline position, the output of the constant speed regulator 410 isconnected to the clutch 106 and the output of the controller 140 isconnected to the clutch 406. And the effect of the potentiometer 175 hasbeen reversed through the change in the position of the switches SS1-1and SS1-2 from the full line position to the dashed line position.

With the switches SS1-1 and SS1-2 in the dashed line position, thepotentiometer 175 is arranged to provide larger negative voltages to ajunction J as the arm 56 is pulled downwardly. So an increasing negativecurrent is effected in the line 158 as the arm 56 is moved progressivelydownwardly. Flux in the clutch 406 is increased by the controller 140and the rotational speed of the pulling wheel 40 is increased.

In operation, with the selector switch SS1 in the dashed line position,the apparatus operates so that the linear rate of strand feed from thepull wheel 40 is matched to predetermined increases in the linear rateof the strand collection. As the diameters of the packages 72 and 74'begin to increase, the increasing strand collection speed shortens thelengths of the strands 26' and 28 between the pulling wheel 40 and thewinder 70. The arm 56 is pulled downwardly to an equilibrium position;here the controller 140 provides a voltage signal having a patterenedrate of change that increases the speed of the pull wheel 40 (throughthe clutch 406) in accordance with the build-up of the package at themoment. But, as the packages 72 and 74' continue to grow in diameter,the linear strand collection rate continues to increase. The strands 26'and 28' move the arm 56 again until a new equilibrium con dition isestablished generally as explained in relation to the operation of theapparatus of FIGS. 1 and 2, except here the rotational speed of thepulling wheel 40 is being generally increased during package formation.

We claim:

1. Apparatus for processing linear material into a wound packagecomprising:

rotary means for linearly feeding the linear material;

means for collecting the fed material, such means including a rotatablecollector for collecting the fed material into a wound package;

control means for supplying a control signal having a patterned rate ofchange effective to modify the rotational speedof the collector to causethe linear rate of collection of the material to approach in general thelinear rate of feed of the material during package build-up on thecollector and for supplying a control signal having a patterned rate ofchange effective to modify the rotational speed of the rotary means tocause the linear rate of feed of the material to approach in general thelinear rate of collection of the material during package buildup on thecollector, the control means including switching means for selectingbetween the two control signals;

means for sensing the differences between the speeds of the rotaryfeeding means and the collector of the collecting means; and

means effective in response to the sensed differences between the speedsto change the patterned rate of the selected control signal to bring thelinear speeds of the rotary means and the collecting means intoconformity.

2. Apparatus for packaging linear material comprising:

rotary means for linearly feeding the linear material;

means for collecting the fed material, such means including a rotatablecollector for collecting the fed material into a wound package;

control means for supplying a control signal having a patterned rate ofchange effective to modify the rotational speed of the collector duringpackage build-up to cause the linear rate of collection of the materialto approach in general the linear rate of feed of the material and forsupplying a control signal having a patterned rate of change effectiveto modify the rotational speed of the rotary means during packagebuild-up to cause the linear rate of feed of the material to approach ingeneral the linear rate of collection of the material, the control meansincluding switching means for selecting between the two control signals;

means for sensing the differences between the speeds of the rotaryfeeding means and the collector of the collecting means; and

means effective in response to the sensed differences between the speedsto bring the linear speeds of the rotary means and the collecting meansinto conformity.

1. Apparatus for processing linear material into a wound packagecomprising: rotary means for linearly feeding the linear material; meansfor collecting the fed material, such means including a rotatablecollector for collecting the fed material into a wound package; controlmeans for supplying a control signal having a patterned rate of changeeffective to modify the rotational speed of the collector to cause thelinear rate of collection of the material to approach in general thelinear rate of feed of the material during package build-up on thecollector and for supplying a control signal having a patterned rate ofchange effective to modify the rotational speed of the rotary means tocause the linear rate of feed of the material to approach in general thelinear rate of collection of the material during package build-up on thecollector, the control means including switching means for selectingbetween the two control signals; means for sensing the differencesbetween the speeds of the rotary feeding means and the collector of thecollecting means; and means effective in response to the senseddifferences between the speeds to change the patterned rate of theselected control signal to bring the linear speeds of the rotary meansand the collecting means into conformity.
 2. Apparatus for packaginglinear material comprising: rotary means for linearly feeding the linearmaterial; means for collecting the fed material, such means including arotatable collector for collecting the fed material into a woundpackage; control means for supplying a control signal having a patternedrate of change effective to modify the rotational speed of the collectorduring package build-up to cause the linear rate of collection of thematerial to approach in general the linear rate of feed of the materialand for supplying a control signal having a patterned rate of changeeffective to modify the rotational speed of the rotary means duringpackage build-up to cause the linear rate of feed of the material toapproach in general the linear rate of collection of the material, thecontrol means including switching means for selecting between the twocontrol signals; means for sensing the differences between the speeds ofthe rotary feeding means and the collector of the collecting means; andmeans effective in response to the sensed differences between the speedsto bring the linear speeds of the rotary means and the collecting meansinto conformity.